US7832298B2 - Countershaft clutch and gear assembly - Google Patents
Countershaft clutch and gear assembly Download PDFInfo
- Publication number
- US7832298B2 US7832298B2 US11/780,313 US78031307A US7832298B2 US 7832298 B2 US7832298 B2 US 7832298B2 US 78031307 A US78031307 A US 78031307A US 7832298 B2 US7832298 B2 US 7832298B2
- Authority
- US
- United States
- Prior art keywords
- clutch
- gear
- countershaft
- assembly
- disposed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related, expires
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H3/097—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts the input and output shafts being aligned on the same axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0004—Transmissions for multiple ratios comprising a power take off shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19223—Disconnectable counter shaft
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19233—Plurality of counter shafts
Definitions
- the present disclosure relates to a clutch and gear assembly and more particularly to a low inertia clutch and gear assembly for use on a countershaft in a dual clutch automatic transmission.
- a relatively new type of automatic transmission is referred to as a dual countershaft or dual clutch transmission (DCT).
- DCT dual countershaft or dual clutch transmission
- a dual countershaft transmission a pair of countershafts or lay shafts are disposed on opposite sides of the common axis of the input shaft and output shaft and in the same plane.
- Typical dual countershaft transmissions are split torque devices in which both countershafts carry load. This, as noted, requires the shafts to be in the same plane.
- only one countershaft carries load at a time.
- the countershafts can be located anywhere around the output shaft providing they do not interfere and provided there is room for the reverse idler.
- the countershafts are mutually exclusively driven by engagement of one of a pair of range clutches operably disposed between the input shaft and a respective one of the countershafts.
- a plurality of gears are secured to and rotate with the output shaft and each output shaft gear is in constant mesh with a one of a plurality of gears freely rotatably supported on the countershafts.
- Synchronizers and clutches selectively engage a single gear with its associated countershaft and the countershaft range clutch is then engaged to transmit torque from the input shaft to the output shaft.
- the synchronizer In order to provide smooth and responsive gear shifts, the synchronizer must quickly adjust the speed of the countershaft to that of the selected gear so that a positive, e.g., dog, clutch can be fully engaged before the range clutch is engaged. If the range clutch engages before the countershaft speed is fully synchronized and the positive clutch is engaged, the engine to drive wheel connection would be lost and synchronizer damage would occur. Accordingly, the synchronizer must act quickly to facilitate engagement of the positive clutch.
- One of the factors affecting synchronizing time is the mass or inertia of the components to be synchronized.
- the mass of the countershaft and that of all components rotating with it has been the object of much attention.
- the countershaft is hollow in order to both reduce its mass and locate the metal that remains in a relatively thin wall, where it can carry the maximum load and torque.
- the benefits of this approach suggest that further effort to reduce the mass of the countershaft and its associated components would be worthwhile and this invention is the result of such effort.
- the present invention provides a low inertia range clutch and gear assembly for disposition on a countershaft of a dual clutch automatic transmission (DCT).
- the assembly includes a gear which is in constant mesh with a gear secured to and/or driven by the input shaft of the transmission and which is freely rotatably disposed on one of the countershafts or lay shafts. Fewer, lower mass or inertia components of the clutch, i.e., the clutch hub and the smaller friction plates are secured to the countershaft whereas more, higher mass or inertia components, i.e., the clutch housing, the larger friction plates, the backing plate, the piston and the return spring, are all mounted on and rotate with the gear.
- the gear also includes a plurality of passages which direct a flow of pressurized hydraulic fluid to the clutch piston. This configuration not only simplifies manufacturing of the countershaft but also improves the centrifugal balance of the piston.
- a synchronizer When a gear shift is commanded, a synchronizer is activated to synchronize the speed of the countershaft with that of the selected gear which is in constant mesh with a gear secured to and rotating with the output shaft.
- a transmission having a range clutch configuration according to the present invention exhibits reduced inertia and thus the countershaft synchronizes more quickly allowing the range clutch to be engaged more guickly and reduce the likelihood of a shift induced transient in the powertrain.
- FIG. 1 is a full sectional view of a portion of a dual clutch transmission incorporating the present invention.
- FIG. 2 is an enlarged, fragmentary sectional view of a range clutch and gear assembly according to the present invention in a dual clutch transmission.
- the dual clutch transmission 10 includes a preferably cast metal housing 12 having various openings, ports, counterbores, shoulders, flanges and other features which receive, support and position the diverse components of the transmission 10 .
- an input shaft 16 which is driven by the output of a torque converter (not illustrated) is rotatably supported on a tapered roller bearing assembly 18 and includes an input drive gear 20 .
- the input drive gear 20 is in constant mesh with a pair of countershaft drive gears, a first countershaft drive gear 22 A and a second countershaft drive gear 22 B.
- Both of the countershaft drive gears 22 A and 22 B are freely rotatably disposed upon a respective pair of countershafts: a first lay shaft or countershaft 24 A and a second lay shaft or countershaft 24 B.
- the forward end of the first countershaft 24 A is rotatably supported by a first tapered roller bearing assembly 26 A and the forward end of the second countershaft 24 B is rotatably supported by a second tapered roller bearing assembly 26 B.
- the opposite (rear) end of the countershaft 24 A is rotatably supported by a respective third tapered roller bearing assembly 28 A and the opposite end of the second countershaft 24 B is rotatably supported by a fourth tapered roller bearing assembly 28 B.
- the countershafts 24 A and 24 B are hollow and define axial lubrication passageways 30 A and 30 B, respectively, which communicate with a plurality of radial passageways 32
- a hollow output shaft or quill 34 is disposed coaxially with the input shaft 16 and is rotatably supported therein at one end by a tapered roller bearing assembly 36 .
- the hollow output shaft or quill 34 receives a drive shaft 38 which is coupled to and driven by the input shaft 16 and directly drives a high/low splitter (not illustrated).
- the output of the high/low splitter drives a prop shaft (not illustrated) typically through a universal joint or other connection (also not illustrated).
- the high/low splitter is optional, however, and may be eliminated in which case the drive shaft 38 may be selectively clutched directly to the output of the transmission 10 to provide a direct, i.e., 1:1, drive ratio.
- Coaxially disposed about the first countershaft 24 A is a first clutch and gear assembly 40 A according to the present invention. Also coaxially disposed about the first countershaft 24 A are a pair of gears 42 and 44 of distinct pitch diameters.
- the gears 42 and 44 as well as the other gears disposed on the countershafts 24 A and 24 B may be helical or spur gears.
- the gears 42 and 44 are freely rotatably disposed on the first countershaft 24 A and are in constant mesh with a respective pair of gears 46 and 48 coupled to and rotating with the output shaft 34 .
- the gears 42 and 46 and the gears 44 and 48 provide two distinct torque or speed ratios between the first countershaft 24 A and the output shaft 34 .
- a first synchronizer and clutch assembly 50 includes a shift fork 52 that is bi-directionally translated by an actuator (not illustrated).
- the first synchronizer and clutch assembly 50 is illustrated in a neutral or disengaged position and may be translated to the left to synchronize the speed of the countershaft 24 A to the speed of the gear 42 and positively couple it thereto or moved to the right to synchronize the speed of the countershaft 24 A to the speed of the gear 44 and positively couple it thereto.
- the second countershaft 24 B includes a second clutch and gear assembly 40 B which is in all respects the same as the first clutch and gear assembly 40 A which will be described below as well as three additional gears 54 , 56 and 58 which are freely rotatably disposed about the second countershaft 24 B.
- Two of the three additional gears 54 and 56 are in constant mesh with two respective gears 62 and 64 which are coupled to and rotate with the output shaft 34 .
- the two additional pairs of gears 54 and 62 and 56 and 64 provide two more forward torque or speed ratios.
- the third additional gear 58 is in constant mesh with an idler gear (not illustrated) which is, in turn, in constant mesh with a gear 66 which is coupled to and rotates with the output shaft 34 .
- a second synchronizer and clutch assembly 68 selectively synchronizes and couples the gears 54 and 56 to the second countershaft 24 B and a third synchronizer and clutch assembly 72 synchronizes and couples the third gear 58 to the second countershaft 24 B.
- the first clutch and gear assembly 40 A includes the first countershaft drive gear 22 A which is preferably supported for rotation on the first countershaft 24 A by a roller bearing assembly 82 .
- the first drive gear 22 A includes gear teeth 84 about its periphery and a plurality of axial fluid passageways 86 extending from one face of the first drive gear 22 A to the other and preferably arranged concentrically about the axis of the first drive gear 22 A and the first countershaft 24 A.
- the axial fluid passageways 86 communicate at one end with a continuous circumferential groove or channel 92 and at the other with an annular cylinder 94 .
- the circumferential groove or channel 92 is flanked by a pair of shallow grooves or channels 96 which each receive a rotating seal 98 .
- the transmission housing 12 includes an annular projection or flange 100 disposed concentrically about the axis of the first drive gear 22 A and the first countershaft 24 A.
- the projection or flange 100 supports and positions a stationary annular sleeve 102 which is in sealing contact with the rotating seals 98 .
- Between the axially spaced-apart circular lines of contact of the rotating seals 98 on the annular sleeve 102 are one or more ports 104 which supply pressurized hydraulic fluid to the annular groove or channel 92 from a passageway 106 which communicates with a source of hydraulic fluid (not illustrated).
- a clutch assembly 110 includes a bell-shaped circular housing 112 which is secured to the first drive gear 22 A by, for example, welding or other positive means which provides a fluid tight seal between the first drive gear 22 A and the circular housing 112 .
- the bell-shaped circular housing 112 includes internal or female splines 114 which engage and drive a first plurality of larger diameter friction clutch plates or discs 116 having complementarily configured external or male splines 118 about their peripheries.
- the first plurality of friction clutch plates or discs 116 are interleaved with a second plurality of smaller diameter clutch plates or discs 122 having internal or female splines 124 .
- each of the clutch plates or discs 116 and 122 includes friction facing material (not illustrated).
- the internal or female splines 124 engage complementarily configured external or male splines 126 disposed on a clutch hub 128 which is coupled to the first countershaft 24 A by a set of interengaging splines 132 and rotates therewith.
- An annular reaction or backing plate 134 is retained in the bell-shaped housing 112 by a snap ring 136 and functions as a stop against which the clutch plates or discs 116 and 122 are compressed.
- the first drive gear 22 A and a portion of the bell-shaped housing 112 cooperatively form and define the annular cylinder 94 which slidingly receives an annular piston 140 .
- the annular piston 140 includes a first outer circumferential channel or groove 142 which receives a first fluid tight seal 144 and the first drive gear 22 A includes a second circumferential channel or groove 146 which receives a second fluid tight seal 148 .
- the fluid tight seals 144 and 148 provide a sliding, fluid tight seal between the annular piston 140 , the first drive gear 22 A and the bell-shaped housing 112 and facilitate axial translation of the annular piston 140 .
- a stepped annular balance piston 152 resides between the piston 140 and the clutch hub 128 and is retained in position by a snap ring 154 .
- a plurality of compression springs 156 are disposed between the annular piston 140 and the stepped annular balance piston 152 and function as return springs to translate the annular piston 140 axially to the left in FIG. 2 when hydraulic fluid pressure is not present in the annular cylinder 94 .
- Other spring configurations such as a Belleville spring or wave washers may be utilized in place of the plurality of compression springs 156 .
- first clutch and gear assembly 40 A specifically locating the clutch housing 112 , the first plurality of larger clutch discs 116 , the reaction plate 134 , the piston 140 , the balance piston 152 and the return spring 156 on the first drive gear 22 A for rotation therewith while locating only the remaining second plurality of smaller clutch discs 122 and the clutch hub 128 on the first countershaft 24 A for rotation therewith, reduces the mass and inertia of the components that must be synchronized during a gear shift and therefore reduces the synchronization time.
- incorporating the hydraulic fluid passageways 86 in the first drive gear 22 A significantly improves the centrifugal balance of the annular piston 140 by introducing the hydraulic fluid to the rotating assembly at a larger radius than if the fluid was supplied through the first countershaft 24 A.
- This improved balance allows loads on the compression springs 156 to be lowered which, in turn, reduces the stress on other clutch components and improves the capacity of the clutch assembly 110 .
- Locating the hydraulic fluid passageways 86 in the first drive gear 22 A also simplifies and therefore reduces the manufacturing cost of the countershafts 24 A and 24 B by eliminating the hydraulic fluid feed passageways in these components.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
Claims (17)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/780,313 US7832298B2 (en) | 2007-07-19 | 2007-07-19 | Countershaft clutch and gear assembly |
DE102008033475.8A DE102008033475B4 (en) | 2007-07-19 | 2008-07-16 | Countershaft coupling and gear assembly |
CN200810137777.7A CN101349327B (en) | 2007-07-19 | 2008-07-18 | Countershaft clutch and gear assembly |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/780,313 US7832298B2 (en) | 2007-07-19 | 2007-07-19 | Countershaft clutch and gear assembly |
Publications (2)
Publication Number | Publication Date |
---|---|
US20090019959A1 US20090019959A1 (en) | 2009-01-22 |
US7832298B2 true US7832298B2 (en) | 2010-11-16 |
Family
ID=40176121
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/780,313 Expired - Fee Related US7832298B2 (en) | 2007-07-19 | 2007-07-19 | Countershaft clutch and gear assembly |
Country Status (3)
Country | Link |
---|---|
US (1) | US7832298B2 (en) |
CN (1) | CN101349327B (en) |
DE (1) | DE102008033475B4 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110079097A1 (en) * | 2009-10-02 | 2011-04-07 | Oerlikon Graziano S.P.A. | Two-speed transmission for electric vehicles |
US20220381214A1 (en) * | 2020-02-23 | 2022-12-01 | Volvo Truck Corporation | Electric machine gearbox and engine starter and power generator including gearbox |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5303318B2 (en) * | 2009-03-06 | 2013-10-02 | 株式会社エフ・シー・シー | Power transmission device |
US8449423B2 (en) * | 2010-11-10 | 2013-05-28 | GM Global Technology Operations LLC | Selectable one-way clutch with breakaway feature |
CN102384248B (en) * | 2011-10-21 | 2013-10-23 | 盛瑞传动股份有限公司 | Gear assembly for automatic transmission case |
CN108302132B (en) * | 2018-01-24 | 2019-07-16 | 中国石油大学胜利学院 | A kind of arrangement of clutch suitable for multiple well pumping unit |
DE102018222007A1 (en) * | 2018-12-18 | 2020-06-18 | Zf Friedrichshafen Ag | Coupling arrangement, dual clutch transmission arrangement and motor vehicle |
CN113685502B (en) * | 2020-05-18 | 2024-01-19 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
CN113685505B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
CN113685507B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
DE102021113560A1 (en) * | 2021-05-26 | 2022-12-01 | Deere & Company | PTO transmission and agricultural utility vehicle |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20020104397A1 (en) * | 2001-02-08 | 2002-08-08 | Bowen Thomas C. | Dual countershaft twin clutch automated transmission with bi-directional clutches |
US6446774B2 (en) * | 2000-04-10 | 2002-09-10 | New Venture Gear, Inc. | Active control of a hydra-mechanical traction control device |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4549443A (en) * | 1983-12-07 | 1985-10-29 | Twin Disc, Incorporated | Multi-speed reversible transmission of countershaft construction |
US5347879A (en) * | 1993-02-09 | 1994-09-20 | General Motors Corporation | Power transmission |
JP4367182B2 (en) * | 2004-03-03 | 2009-11-18 | トヨタ自動車株式会社 | Planetary gear set |
JP4412080B2 (en) * | 2004-07-06 | 2010-02-10 | トヨタ自動車株式会社 | Automatic transmission clutch device |
-
2007
- 2007-07-19 US US11/780,313 patent/US7832298B2/en not_active Expired - Fee Related
-
2008
- 2008-07-16 DE DE102008033475.8A patent/DE102008033475B4/en not_active Expired - Fee Related
- 2008-07-18 CN CN200810137777.7A patent/CN101349327B/en not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6446774B2 (en) * | 2000-04-10 | 2002-09-10 | New Venture Gear, Inc. | Active control of a hydra-mechanical traction control device |
US20020104397A1 (en) * | 2001-02-08 | 2002-08-08 | Bowen Thomas C. | Dual countershaft twin clutch automated transmission with bi-directional clutches |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110079097A1 (en) * | 2009-10-02 | 2011-04-07 | Oerlikon Graziano S.P.A. | Two-speed transmission for electric vehicles |
US8984976B2 (en) * | 2009-10-02 | 2015-03-24 | Oerlikon Graziano S.P.A. | Two-speed transmission for electric vehicles |
US20220381214A1 (en) * | 2020-02-23 | 2022-12-01 | Volvo Truck Corporation | Electric machine gearbox and engine starter and power generator including gearbox |
US11976620B2 (en) * | 2020-02-23 | 2024-05-07 | Volvo Truck Corporation | Electric machine gearbox and engine starter and power generator including gearbox |
Also Published As
Publication number | Publication date |
---|---|
CN101349327A (en) | 2009-01-21 |
DE102008033475A1 (en) | 2009-02-05 |
DE102008033475B4 (en) | 2017-05-18 |
US20090019959A1 (en) | 2009-01-22 |
CN101349327B (en) | 2012-04-25 |
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